EP0039320A2 - Vibrationless impact tool - Google Patents
Vibrationless impact tool Download PDFInfo
- Publication number
- EP0039320A2 EP0039320A2 EP81850076A EP81850076A EP0039320A2 EP 0039320 A2 EP0039320 A2 EP 0039320A2 EP 81850076 A EP81850076 A EP 81850076A EP 81850076 A EP81850076 A EP 81850076A EP 0039320 A2 EP0039320 A2 EP 0039320A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- cylinder
- valve member
- relative
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
- B25D17/24—Damping the reaction force
- B25D17/245—Damping the reaction force using a fluid
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/16—Valve arrangements therefor
Definitions
- This invention relates to an impact t'ool comprising a housing, a cylinder axially movable in said housing, a hammer piston provided with pressurized fluid-operated reciprocable drive means arranged for reciprocably driving said hammer piston relative to said cylinder, a cushioning space for containing a recoil cushioning volume of air between the cylinder and the housing, and a pressure regulating means for controlling the supply and venting of air, to and from, respectively, the cushioning space and for balancing the pressure within the cushioning space relative to an actual forward feeding force applied to the housing in use of the tool.
- This type of pressure regulating means is, however, disadvantageous in that, in addition to the continuous air relief'flow determined by the degree of compression of the relief valve biasing spring, it momentarily vents air to the atmosphere in order to avoid the build up of pressure peaks during recoil of the cylinder.
- the above type of pressure regulating. means does not permit the air in the cushioning chamber itself to be used as a resiliently deformable and, in use, deformed, spring means and thus itself, together with the cylinder and the housing, form a spring-mass vibration dampening system.
- the present invention provides an impact tool comprising a housing, a cylinder axially movable in the housing, a hammer piston reciprocably driven by pressure fluid in the cylinder, a recoil cushioning space arranged between the cylinder and the housing and a pressure regulating means for controlling the supply and venting of air to and from, respectively, the cushioning space and for balancing the pressure within the cushioning space restive to an actual forward feeding force applied to the housing in use of the tool, characterized in that said pressure regulating means comprises a first part located in a fixed disposition relative to said housing and a second part located in a fixed disposition relative to said cylinder, said first and second parts being formed and arranged so .that changes in the relative positions therebetween corresponding to changes in the relative axial positions of said housing and cylinder controls the supply and venting of air, to and from the cushioning space, respectively.
- Fig. 1 shows a hand held riveting tool which is intended to be supported in one hand, in use thereof.
- the tool comprises a housing 10 which is formed with a pistol grip 11 and which guidedly supports an axially movable cylinder 12..At its forward end, the housing 10 is provided with a tool receiving opening (not shown) into which is fed the rear end of a rivet punch 13. The latter is axially secured to the cylinder 12 by means of a wire-type tool retainer 14.
- a quick release coupling nipple 15 for connection of the tool to a pressurized air source.
- a throttle valve (not shown) which is operable by a trigger 16.
- the impact mechanism of the tool shown in the drawings is of conventional design and does not constitute a part of the novel features of the present invention. Accordingly the impact mechanism will not be illustrated or described in any great detail.
- the impact mechanism comprises a cylinder 12 and hammer piston 17 operated by pressurized air within said cylinder 12.
- the reciprocating movement of the hammer piston 17 is controlled by an air distribution valve in a conventional manner similar to that used in known impact mechanisms of this type. Exhaust air is vented to the atmosphere through outlet openings 18.
- the cylinder 12 At its rear end, the cylinder 12 is provided with a rigid tubular extension 1'9 threadedly engaging an annular end closure 20.
- a generally cup shaped support member 21 is located within the tubular extension 19 coaxially with the cylinder 12. The support member 21 is kept in place by the end 'closure 20. Between the tubular extension 19 and the support member 21 there is formed the air inlet passage of the abovementioned impact mechanism which passage communicates with the downstream side of the throttle valve in the pistol grip 11 through an opening.
- a damping unit 24 which comprises a rear end wall 25 and a tubular valve housing 26 formed integrally with the end wall 25 and extending coaxially with the cylinder 12 and the support member 21.
- the valve housing 26 defines a cylindrical valve chamber 27 into whose forward end the support member 21 is able to enter.
- valve housing 26 Adjacent the rear end wall 25, the valve housing 26 is provided with a number of radial openings 28 communicating with an annular chamber 30 in the housing 10.
- the chamber 30 is in turn maintained in continuous communication with a further chamber 29 in the pistol grip 11 via a passage 31 in the housing 10.
- the further chamber 29, the annular chamber 30 and the valve chamber 27 and their interconnecting passages 28, 31 together constitute a recoil cushioning space.
- valve housing 26 Close to its forward end, the valve housing 26 has a number of air vent ports 32 connecting.the valve chamber 27 with a venting space 33 which surrounds the valve housing 26 and.is connected to the atmosphere through outlet openings 34.
- air supply ports 35 which are connected, via passages 36 and 37 (illustrated in dash lines), to the main pressurized air supply passage of the tool upstream of the trigger (16) operated throttle valve.
- valve chamber 27 there is located a cup shaped piston-like valve member 38 disposed with its end wall 39 (see Fig. 4) in'abutment with the rear end of the support member 21.
- a resilient biasing means in the form of a coil type compression spring 40 has one end disposed inside the valve member 38 and its other end in abutment with the rear end wall 25 of the housing 10 so that the spring 40 biases the valve member 38, as well as the support member 21 and the cylinder 12 therethrough, in the forward feeding direction of the tool.
- the valve member 38 is formed with an annular waist 42 defining, together with the valve housing 26 a control chamber therebetween.
- the waist 42 has opposed frusto-conical end portions 43 and 44 (see Fig. 4) which define with the valve housing 26 tapered end portions of the control chamber for providing a smoothly continuously variable ranges of opening and closing of the air supply and vent ports (35, 32) during reciprocation of the valve member (38) in order to accomplish an as accurate as possible pressure balancing in the valve chamber 27 and, in fact, in the entire recoil cushioning space .
- the valve member 38 is provided with two radial openings 46 ' through which the annular chamber defined between the annular waist 42 and the valve housing 26, communicates with the valve chamber 27. '
- the width of the waist 42 (axially of the valve member 38) relative to the axial separation of the air supply ports 35 and the air vent ports 32 is selected to be such that an optimum regulation of the pressure within the recoil cushioning space is obtained.
- the port locations (35, 32) and the width of the waist 42 are such that supply and drainage of air to the valve chamber 27 can take place simultaneously in an intermediate position of the valve member 38 as shown in Fig. 4.
- the inlet nipple 15 is connected up to a pressurized air supply and pressurized air fed to the supply port 35 via the passages 36, 37.
- the cylinder 12 In the starting position of the tool, i.e. when no forward feeding force is applied on the tool housing 10, the cylinder 12 is kept in its forwardmost position relative to the housing 10, with respect to the forward feeding direction by means of the spring 40 acting between the rear end wall 25 of the housing 10 and the valve member 38. Since the latter continuously abuts against the support member 21, the forwardly directed biasing force exerted by the spring 40 is directly transferred to the cylinder 12.
- a working position of the cylinder 12 relative to the housing 10 can be found in which the frusto-conical end portions 43 and 44 of the valve member waist 42, control opening and closing of the supply and drainage ports 35 and 32, respectively, in such a manner that the pressure within the cushioning space is continuously balanced relative to the actual feeding force acting on the housing, or more specifically, so that the force exerted by-the cushioning space pressure on the valve member 38 together with the force exerted by the spring 40 thereon equal the force applied to the housing 10 by the operator.
- valve member 38 If, however, the feeding or backing force on the housing 10 is too great, the valve member 38 is displaced to its rearmost or full-load position, in which the air vent ports 32 are completely occluded by the valve member 38 and the supply ports 35 are fully opened to the annular waist 42. This means that the full pressure of the pressurized air source is developed in the cushioning space.
- the operational properties of the recoil cushioning arrangement of the above tool of the invention are characterized by an arcuate and continuous adjustment of the static cushioning volume pressure over a wide range of tool feeding forces and a very effective recoil and vibration-absorption throughout the static pressure range of the cushioning space.
- the outstanding dynamic force absorption properties of the cushioning arrangement of the invention are due to the use of a relatively large cushioning space.
- the total spring constant of the relatively large volume of air in the cushioning space and the spring 40 is preferably adapted with respect to the masses of the cylinder 12 and the housing 10 so that the-resonant frequency of the system is considerably less than the vibration frequency of the impact mechanism.
Abstract
Description
- . This invention relates to an impact t'ool comprising a housing, a cylinder axially movable in said housing, a hammer piston provided with pressurized fluid-operated reciprocable drive means arranged for reciprocably driving said hammer piston relative to said cylinder, a cushioning space for containing a recoil cushioning volume of air between the cylinder and the housing, and a pressure regulating means for controlling the supply and venting of air, to and from, respectively, the cushioning space and for balancing the pressure within the cushioning space relative to an actual forward feeding force applied to the housing in use of the tool.
- An impact tool of the above type is disclosed in U.S. Patent No. 3,727,700. This known tool, however, employs a vibration cushioning chamber which is continuously supplied with pressurized air and in which the air pressure is controlled by a spring biased relief valve mechanism. The opening pressure of the latter is determined by the degree of compression of the relief valve biasing spring, which in turn depends on the forward feeding force applied to the tool housing.
- This type of pressure regulating means is, however, disadvantageous in that, in addition to the continuous air relief'flow determined by the degree of compression of the relief valve biasing spring, it momentarily vents air to the atmosphere in order to avoid the build up of pressure peaks during recoil of the cylinder. Thus the above type of pressure regulating. means does not permit the air in the cushioning chamber itself to be used as a resiliently deformable and, in use, deformed, spring means and thus itself, together with the cylinder and the housing, form a spring-mass vibration dampening system.
- It is an object of the present invention to avoid or minimize one or more of the above disadvantages and to provide an impact tool with an improved pressure regulating means.
- The present invention provides an impact tool comprising a housing, a cylinder axially movable in the housing, a hammer piston reciprocably driven by pressure fluid in the cylinder, a recoil cushioning space arranged between the cylinder and the housing and a pressure regulating means for controlling the supply and venting of air to and from, respectively, the cushioning space and for balancing the pressure within the cushioning space restive to an actual forward feeding force applied to the housing in use of the tool, characterized in that said pressure regulating means comprises a first part located in a fixed disposition relative to said housing and a second part located in a fixed disposition relative to said cylinder, said first and second parts being formed and arranged so .that changes in the relative positions therebetween corresponding to changes in the relative axial positions of said housing and cylinder controls the supply and venting of air, to and from the cushioning space, respectively.
- In a tool of the present invention there can be obtained an improved damping by using a volume of air in the cushioning space itself as an additional spring means.
- Further preferred features and advantages of the invention will appear from the following description given by way of example of a preferred embodiment illustrated with reference to the accompanying drawings in which:
- Fig. 1 is a partly sectioned side elevation of a pneumatic impact tool of the invention;
- Fig. 2 is a partly sectioned detail side view on an enlarged scale, of the rear end portion of the tool shown in Fig. 1 in its rest position;
- Fig. 3 is a corresponding view but with the cylinder and the pressure regulating means of the tool in their full load positions;
- Fig. 4 is a further detail sectional view, on a still larger scale, of the pressure regulating means of Figs. 1 to 3.
- Fig. 1 shows a hand held riveting tool which is intended to be supported in one hand, in use thereof. The tool comprises a
housing 10 which is formed with apistol grip 11 and which guidedly supports an axiallymovable cylinder 12..At its forward end, thehousing 10 is provided with a tool receiving opening (not shown) into which is fed the rear end of a rivet punch 13. The latter is axially secured to thecylinder 12 by means of a wire-type tool retainer 14. - At the lower end of the
pistol grip 11, there is mounted a quickrelease coupling nipple 15 for connection of the tool to a pressurized air source. Within thepistol grip 11 there is lodged a throttle valve (not shown) which is operable by atrigger 16. - The impact mechanism of the tool shown in the drawings is of conventional design and does not constitute a part of the novel features of the present invention. Accordingly the impact mechanism will not be illustrated or described in any great detail. Briefly, the impact mechanism comprises a
cylinder 12 and hammer piston 17 operated by pressurized air within saidcylinder 12. The reciprocating movement of the hammer piston 17 is controlled by an air distribution valve in a conventional manner similar to that used in known impact mechanisms of this type. Exhaust air is vented to the atmosphere throughoutlet openings 18. - At its rear end, the
cylinder 12 is provided with a rigid tubular extension 1'9 threadedly engaging an annular end closure 20. A generally cupshaped support member 21 is located within thetubular extension 19 coaxially with thecylinder 12. Thesupport member 21 is kept in place by the end 'closure 20. Between thetubular extension 19 and thesupport member 21 there is formed the air inlet passage of the abovementioned impact mechanism which passage communicates with the downstream side of the throttle valve in thepistol grip 11 through an opening. - In the rear part of the
housing 10, there is provided adamping unit 24 which comprises arear end wall 25 and atubular valve housing 26 formed integrally with theend wall 25 and extending coaxially with thecylinder 12 and thesupport member 21. Thevalve housing 26 defines acylindrical valve chamber 27 into whose forward end thesupport member 21 is able to enter. - Adjacent the
rear end wall 25, thevalve housing 26 is provided with a number ofradial openings 28 communicating with an annular chamber 30 in thehousing 10. The chamber 30 is in turn maintained in continuous communication with afurther chamber 29 in thepistol grip 11 via apassage 31 in thehousing 10. Thefurther chamber 29, the annular chamber 30 and thevalve chamber 27 and theirinterconnecting passages - Close to its forward end, the
valve housing 26 has a number ofair vent ports 32 connecting.thevalve chamber 27 with a venting space 33 which surrounds thevalve housing 26 and.is connected to the atmosphere through outlet openings 34. - Between the
air vent ports 32 and theradial openings 28, there is provided a number ofair supply ports 35 which are connected, viapassages 36 and 37 (illustrated in dash lines), to the main pressurized air supply passage of the tool upstream of the trigger (16) operated throttle valve. - Within the
valve chamber 27, there is located a cup shaped piston-like valve member 38 disposed with its end wall 39 (see Fig. 4) in'abutment with the rear end of thesupport member 21. A resilient biasing means in the form of a coiltype compression spring 40 has one end disposed inside thevalve member 38 and its other end in abutment with therear end wall 25 of thehousing 10 so that thespring 40 biases thevalve member 38, as well as thesupport member 21 and thecylinder 12 therethrough, in the forward feeding direction of the tool. - The
valve member 38 is formed with anannular waist 42 defining, together with the valve housing 26 a control chamber therebetween. Thewaist 42 has opposed frusto-conical end portions 43 and 44 (see Fig. 4) which define with thevalve housing 26 tapered end portions of the control chamber for providing a smoothly continuously variable ranges of opening and closing of the air supply and vent ports (35, 32) during reciprocation of the valve member (38) in order to accomplish an as accurate as possible pressure balancing in thevalve chamber 27 and, in fact, in the entire recoil cushioning space . Within theannular waist 42 thevalve member 38 is provided with tworadial openings 46' through which the annular chamber defined between theannular waist 42 and thevalve housing 26, communicates with thevalve chamber 27.' - The width of the waist 42 (axially of the valve member 38) relative to the axial separation of the
air supply ports 35 and theair vent ports 32 is selected to be such that an optimum regulation of the pressure within the recoil cushioning space is obtained. As shown in Fig. 4, the port locations (35, 32) and the width of thewaist 42 are such that supply and drainage of air to thevalve chamber 27 can take place simultaneously in an intermediate position of thevalve member 38 as shown in Fig. 4. - In use of the riveting tool the
inlet nipple 15 is connected up to a pressurized air supply and pressurized air fed to thesupply port 35 via thepassages tool housing 10, thecylinder 12 is kept in its forwardmost position relative to thehousing 10, with respect to the forward feeding direction by means of thespring 40 acting between therear end wall 25 of thehousing 10 and thevalve member 38. Since the latter continuously abuts against thesupport member 21, the forwardly directed biasing force exerted by thespring 40 is directly transferred to thecylinder 12. By pulling thetrigger 16 pressurized air is then supplied to the impact mechanism., If, however, the rivet punch 13 is not applied to a rivet and'no feeding force is exerted on thehousing 10, the relative'positions of thehousing 10 and thecylinder 12 remain unchanged. This means that theair supply ports 35 are occluded by thevalve member 38 and pressurized air is unable to pass into thevalve chamber 27 via theannular waist 42 andradial openings 46 of thevalve member 38. In this no-load position, illustrated in Figs. 1 and 2, theair vent ports 32 are open to thewaist 42, which means that thevalve chamber 27 and the entire recoil cushioning space are vented to the atmosphere and pressure does not build up in the cushioning space - If a normal operating force is applied to the
housing 10 by an operator, a working position of thecylinder 12 relative to thehousing 10 can be found in which the frusto-conical end portions 43 and 44 of thevalve member waist 42, control opening and closing of the supply anddrainage ports valve member 38 together with the force exerted by thespring 40 thereon equal the force applied to thehousing 10 by the operator. - If, however, the feeding or backing force on the
housing 10 is too great, thevalve member 38 is displaced to its rearmost or full-load position, in which theair vent ports 32 are completely occluded by thevalve member 38 and thesupply ports 35 are fully opened to theannular waist 42. This means that the full pressure of the pressurized air source is developed in the cushioning space. - .The operational properties of the recoil cushioning arrangement of the above tool of the invention are characterized by an arcuate and continuous adjustment of the static cushioning volume pressure over a wide range of tool feeding forces and a very effective recoil and vibration-absorption throughout the static pressure range of the cushioning space.
- The outstanding dynamic force absorption properties of the cushioning arrangement of the invention are due to the use of a relatively large cushioning space. The total spring constant of the relatively large volume of air in the cushioning space and the
spring 40 is preferably adapted with respect to the masses of thecylinder 12 and thehousing 10 so that the-resonant frequency of the system is considerably less than the vibration frequency of the impact mechanism. By using air supply andair vent ports cylinder 12 induced by the recoil action of the impact mechanism. This means that the dynamic pressure variations are absorbed by the air volume in the cushioning space in a substantially elastic manner, the air-volume forming the spring of a mass-spring-mass vibration dampening system in which the two masses are on the one hand thecylinder 12 and on the other hand thehousing 10.
Claims (15)
characterized in that
said pressure regulating means (26,38) comprises a first part (26) located in a fixed disposition relative to said housing (10) and a second part (38) located in a fixed disposition relative to said cylinder (12), said first and second parts (26,38) being formed and arranged so that changes in the relative positions therebetween corresponding to changes in the relative axial positions of said housing (10) and cylinder (12) controls the supply and venting of air, to and from the cushioning space (27-31), respectively.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE8003177A SE421182B (en) | 1980-04-25 | 1980-04-25 | VIBRATION DUMP DEVICE TOOL |
SE8003177 | 1980-04-25 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0039320A2 true EP0039320A2 (en) | 1981-11-04 |
EP0039320A3 EP0039320A3 (en) | 1982-02-03 |
EP0039320B1 EP0039320B1 (en) | 1984-08-15 |
Family
ID=20340843
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP81850076A Expired EP0039320B1 (en) | 1980-04-25 | 1981-04-24 | Vibrationless impact tool |
Country Status (10)
Country | Link |
---|---|
US (1) | US4388972A (en) |
EP (1) | EP0039320B1 (en) |
JP (1) | JPS5733979A (en) |
AU (1) | AU541699B2 (en) |
CA (1) | CA1154333A (en) |
CS (1) | CS257753B2 (en) |
DE (1) | DE3165514D1 (en) |
FI (1) | FI74419C (en) |
SE (1) | SE421182B (en) |
SU (1) | SU1118282A3 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1993006972A1 (en) * | 1991-10-09 | 1993-04-15 | Sovmestnoe Sovetsko-Finskoe Predpriyatie Rpf-D | Pneumatic hammer |
US5587469A (en) * | 1990-01-11 | 1996-12-24 | Isis Pharmaceuticals, Inc. | Oligonucleotides containing N-2 substituted purines |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE438465B (en) * | 1980-12-18 | 1985-04-22 | Atlas Copco Ab | GREAT PROGRAM WITH OPTIONAL ADJUSTMENT FOR PERFORMANCE TOOLS |
JPS61144979U (en) * | 1985-02-26 | 1986-09-06 | ||
US4708759A (en) * | 1985-09-30 | 1987-11-24 | Crathern Engineering Co., Inc. | Edge locating device |
JPS6261259U (en) * | 1985-10-08 | 1987-04-16 | ||
JPS62108963U (en) * | 1985-12-19 | 1987-07-11 | ||
US4776408A (en) * | 1987-03-17 | 1988-10-11 | Deutsch Fastener Corporation | Pneumatic impact tool |
WO1993009919A1 (en) * | 1991-11-11 | 1993-05-27 | Nauchno-Tekhnichesky Kooperativ 'tekhprogress' | Pneumatic instrument |
WO1993020981A1 (en) * | 1992-04-10 | 1993-10-28 | Nauchno-Tekhnichesky Kooperativ 'tekhprogress' | Pneumatic instrument |
DE10005080C1 (en) * | 2000-02-04 | 2001-08-02 | Bosch Gmbh Robert | Hand tool has handle with handle part fixed to casing by elastic, vibration-damping element and fixing part fixed at elastic element |
DE10145464C2 (en) * | 2001-09-14 | 2003-08-28 | Wacker Construction Equipment | Drill and / or impact hammer with idle control depending on the contact pressure |
WO2005007351A1 (en) * | 2003-07-15 | 2005-01-27 | Wacker Construction Equipment Ag | Working tool with damped handle |
TWM258839U (en) * | 2004-05-21 | 2005-03-11 | Chen Shiou Ru | Airflow controlling structure of pneumatic tool |
AT501861B1 (en) * | 2005-05-25 | 2009-08-15 | Bbg Baugeraete Gmbh | HAND-HELD, VIBRATION-STEAMED AIR HAMMER |
TWM296773U (en) * | 2006-03-31 | 2006-09-01 | Shuen Tai Prec Entpr Co Ltd | Portable power drill with shock absorption protective sheath |
US7878265B2 (en) * | 2007-02-06 | 2011-02-01 | Makita Corporation | Impact power tool |
JP4815362B2 (en) * | 2007-02-06 | 2011-11-16 | 株式会社マキタ | Impact type work tool |
US7806201B2 (en) * | 2007-07-24 | 2010-10-05 | Makita Corporation | Power tool with dynamic vibration damping |
US8196675B2 (en) * | 2010-03-24 | 2012-06-12 | Sing Hua Industrial Co., Ltd. | Impact hammer with pre-pressing damping and buffering effect |
WO2012058279A2 (en) * | 2010-10-26 | 2012-05-03 | Honsa Thomas W | Tool |
JP5535051B2 (en) * | 2010-11-22 | 2014-07-02 | 株式会社マキタ | Power tools |
US9844867B2 (en) * | 2015-03-24 | 2017-12-19 | Chih Kuan Hsieh | Cushion device for cylinder of pneumatic tool |
US10335938B2 (en) * | 2015-03-24 | 2019-07-02 | Chih Kuan Hsieh | Cushion device for cylinder of pneumatic tool |
CN113153964A (en) * | 2020-01-22 | 2021-07-23 | 大里兴业股份有限公司 | Vibration damping structure of pneumatic hammer |
US11628550B2 (en) * | 2020-02-07 | 2023-04-18 | Storm Pneumatic Tool Co., Ltd. | Vibration reducing structure of pneumatic hammer |
TWI778908B (en) * | 2022-01-21 | 2022-09-21 | 大里興業股份有限公司 | Pneumatic impact tool with improved damping structure |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1827647A (en) * | 1928-11-09 | 1931-10-13 | Galaz Juan | Attachment for pneumatic hammers |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1804712A (en) * | 1930-08-04 | 1931-05-12 | Herman A Stevens | Pneumatic hammer |
US3010431A (en) * | 1960-01-05 | 1961-11-28 | Atlas Copco Ab | Percussion tools |
NL288658A (en) * | 1962-09-11 | |||
US3255832A (en) * | 1962-11-27 | 1966-06-14 | Leavell Charles | Vibrationless percussive tool |
US3727700A (en) * | 1971-04-19 | 1973-04-17 | Chicago Pneumatic Tool Co | Pneumatically percussive tool having a vibration free handle |
US3920086A (en) * | 1974-05-23 | 1975-11-18 | Albert Adolfovich Goppen | Pneumatic hammer |
FR2456593A1 (en) * | 1979-05-15 | 1980-12-12 | Montabert Roger | VIBRATION DAMPER FOR PNEUMATIC PERCUSSION APPARATUS |
-
1980
- 1980-04-25 SE SE8003177A patent/SE421182B/en not_active IP Right Cessation
-
1981
- 1981-04-21 US US06/256,148 patent/US4388972A/en not_active Expired - Lifetime
- 1981-04-22 FI FI811255A patent/FI74419C/en not_active IP Right Cessation
- 1981-04-24 EP EP81850076A patent/EP0039320B1/en not_active Expired
- 1981-04-24 SU SU813276211A patent/SU1118282A3/en active
- 1981-04-24 DE DE8181850076T patent/DE3165514D1/en not_active Expired
- 1981-04-24 JP JP6151481A patent/JPS5733979A/en active Granted
- 1981-04-24 CS CS813080A patent/CS257753B2/en unknown
- 1981-04-24 CA CA000376176A patent/CA1154333A/en not_active Expired
- 1981-04-24 AU AU69830/81A patent/AU541699B2/en not_active Ceased
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1827647A (en) * | 1928-11-09 | 1931-10-13 | Galaz Juan | Attachment for pneumatic hammers |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5587469A (en) * | 1990-01-11 | 1996-12-24 | Isis Pharmaceuticals, Inc. | Oligonucleotides containing N-2 substituted purines |
WO1993006972A1 (en) * | 1991-10-09 | 1993-04-15 | Sovmestnoe Sovetsko-Finskoe Predpriyatie Rpf-D | Pneumatic hammer |
Also Published As
Publication number | Publication date |
---|---|
FI811255L (en) | 1981-10-26 |
AU6983081A (en) | 1981-10-29 |
CS257753B2 (en) | 1988-06-15 |
CA1154333A (en) | 1983-09-27 |
US4388972A (en) | 1983-06-21 |
SE421182B (en) | 1981-12-07 |
AU541699B2 (en) | 1985-01-17 |
SE8003177L (en) | 1981-10-26 |
FI74419C (en) | 1988-02-08 |
FI74419B (en) | 1987-10-30 |
JPS6350150B2 (en) | 1988-10-06 |
SU1118282A3 (en) | 1984-10-07 |
EP0039320B1 (en) | 1984-08-15 |
EP0039320A3 (en) | 1982-02-03 |
JPS5733979A (en) | 1982-02-24 |
DE3165514D1 (en) | 1984-09-20 |
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